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WO1998033688A1 - Vanne de regulation de pression - Google Patents

Vanne de regulation de pression Download PDF

Info

Publication number
WO1998033688A1
WO1998033688A1 PCT/EP1998/000444 EP9800444W WO9833688A1 WO 1998033688 A1 WO1998033688 A1 WO 1998033688A1 EP 9800444 W EP9800444 W EP 9800444W WO 9833688 A1 WO9833688 A1 WO 9833688A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
slide
wheel brake
control valve
way control
Prior art date
Application number
PCT/EP1998/000444
Other languages
German (de)
English (en)
Inventor
Johann Jungbecker
Manfred Rüffer
Original Assignee
Itt Manufacturing Enterprises, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Itt Manufacturing Enterprises, Inc. filed Critical Itt Manufacturing Enterprises, Inc.
Publication of WO1998033688A1 publication Critical patent/WO1998033688A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3655—Continuously controlled electromagnetic valves
    • B60T8/366—Valve details
    • B60T8/367—Seat valves, e.g. poppet valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
    • B60T15/02—Application and release valves
    • B60T15/025—Electrically controlled valves
    • B60T15/028—Electrically controlled valves in hydraulic systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3655—Continuously controlled electromagnetic valves
    • B60T8/366—Valve details
    • B60T8/3665—Sliding valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5018—Pressure reapplication using restrictions
    • B60T8/5025—Pressure reapplication using restrictions in hydraulic brake systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5087—Pressure release using restrictions
    • B60T8/5093—Pressure release using restrictions in hydraulic brake systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors

Definitions

  • the invention relates to an electromagnetically controllable multi-way control valve for slip-controlled hydraulic motor vehicle brake systems for establishing a pressure medium connection between at least one wheel brake and a high-pressure source or a low-pressure accumulator, comprising a slide guided in a sleeve-shaped housing body, which is biased in the longitudinal direction of displacement and one extending in the longitudinal direction Opening, wherein in normal braking operation the bias towards a first end position dominates, in which the wheel brake is fluidly connected to the high-pressure source and is fluidly separated from the low-pressure accumulator, and a valve provided between the wheel brake and the low-pressure accumulator, which is used to reduce pressure in the wheel brake is opened.
  • Such a multi-way valve is known for example from DE 44 41 150 AI.
  • The is in normal braking mode Slider in such a position that a radial opening in the sleeve-shaped housing body, which forms a connection for the high-pressure source, is in pressure medium connection with another opening located in the region of the slide end, which forms a connection for a wheel brake.
  • the slide is designed as a hollow slide, so that the fluid connection of the high pressure source and the wheel brake leads through the longitudinal opening of the slide. If measured wheel sensors of the electrical control and regulating unit of a slip-controlled motor vehicle brake system determine that the wheel is locked, an electromagnetic actuator is energized so that an armature of the electromagnetic actuator is moved in the longitudinal direction of the slide.
  • the armature acts on the slide via a push rod and adjusts it in such a way that the pressure medium connection between the high pressure source and the wheel brake is interrupted. Then the plunger which engages through the slide strikes against a spherical valve closing member and lifts it off its sealing seat, whereby a pressure medium connection between the wheel brake and the low-pressure accumulator is opened to reduce the pressure in the wheel brake.
  • the slide In multi-way valves of the type mentioned at the beginning, as well as in the multi-way valve described above, the slide remains in the above-described position in normal braking operation. Because sometimes it takes a very long time can, until the normal brake operation is exited via the control or regulating device of the brake system and the wheel brake is to be connected to the low-pressure accumulator in order to reduce the pressure, there is sometimes the risk that the slide sticks in its normal brake position, so that rapid pressure reduction in the wheel brake does not occur can be achieved without delay in the desired manner.
  • the above invention is therefore based on the object of eliminating the risk of the slide sticking in its normal braking position for a multi-way pressure control valve of the type described in the introduction.
  • a multi-way pressure control valve of the type mentioned according to the invention in that a slowly displaceable pressure piston is provided in the opening of the slide, which counteracts the bias directed into the first end position with its free end in normal braking operation, so that the slide depends on Pressure of the high pressure source is reciprocable in the longitudinal direction.
  • the pressure piston which is displaceable in the longitudinal opening, is displaced with ever increasing force in the direction of the mouth of the opening and can thus counteract the preload directed in the direction of the first end position, so that the slide is moved slightly counter to the preload, for that to apply the appropriate equilibrium position. If the control pressure is reduced, the spool is slightly moved back under the effect of the preload. According to the invention, a slight back and forth movement of the slide is achieved in normal braking operation, so that there is no risk that the slide will become stuck.
  • the bias in the direction of the first end position is transmitted from a spring means via a mediator element to the slide, and the pressure piston which is longitudinally displaceable in the slide opening is supported against the mediator element.
  • the pressure piston With increasing control pressure in the longitudinal opening of the slide, the pressure piston now presses with increasing force against the mediator element, so that the slide with the mediator element moves against the force of the spring means.
  • the mediator element is formed by an armature of an electromagnetic actuating device, which in the de-energized state of the actuating device, i. H. in normal braking operation, is biased towards an end position.
  • the longitudinal opening of the slide opens at its end facing away from the pressure piston on the end face of the slide there, and in the mouth region of the opening, a pin which moves to a limited extent engages, which connects the valve mentioned above between the wheel brake and Low pressure accumulator keeps closed during normal braking. Due to the limited longitudinal displaceability of the pin, the valve remains closed in normal braking operation even when the slide is moved back and forth in the inventive manner described above.
  • the longitudinally displaceable pin is biased in the closing direction of the valve in normal braking operation by the pressure of the high-pressure source in the opening and is supported against the housing body via the valve.
  • the valve is preferably between the wheel brake and Low-pressure accumulator designed as a seat valve and the valve body of the seat valve can be actuated from the free end of the longitudinally displaceable pin which projects from the longitudinal opening.
  • the free end of the longitudinally displaceable pin itself forms the valve body of the seat valve and, in normal braking operation, lies sealingly against a sealing seat of the seat valve.
  • the free end of the longitudinally displaceable pin is designed in the form of a sealing pin.
  • the longitudinal displaceability of the pin could in any way be limited in order to prevent the pin from sliding out of the longitudinal opening of the slide.
  • the pin has a radial projection which can be placed against a stop to limit the longitudinal displacement.
  • the projection is preferably arranged such that it comes to lie outside the opening.
  • the stop which is also to be provided in this case outside the opening can then be achieved in a technically simple manner by a cup-shaped element placed against the end face of the slide, which has a bottom opening through which the pin slidably engages, but which are not passed by the radial projection of the pin can.
  • a longitudinally displaceable piston-like pressure transmission part bearing against the inwardly facing end face of the longitudinally displaceable pin.
  • the multi-way pressure control valve shown in longitudinal section in the figure comprises a sleeve-shaped housing body 2 and a slide 6 which is displaceable therein in the longitudinal direction 4.
  • the slide 6 is prestressed in the longitudinal direction 4 in opposite directions, namely in the direction of the first end position shown by a first spring 8 and in the opposite direction by a second spring 10.
  • the first spring 8 is supported at one end against a core 12 and at the other end against an armature 14 of an electromagnetic actuating device 16.
  • the armature 14 bears with its side facing away from the spring 8 against an end face 18 of the slide 6.
  • the core 12 of the electromagnetic actuator 16 is held in a press fit by means of a pot-shaped holding element 20, which is placed over a free end 22 of the sleeve-shaped housing body 2 and is sealed off from it.
  • a coil holder 24 with a coil 26 of the electromagnetic actuating device 16 is arranged on the circumference of the cup-shaped element 20.
  • the armature 14, which is displaceable in the longitudinal direction 4 within the cylindrical end section 22 of the housing body 2 is moved against the core 12 against the bias by the spring 8.
  • openings 28, 30, 32 which are spaced apart in the radial direction and form a pressure medium connection to a low-pressure accumulator, a wheel brake or a high-pressure source in the form of a tandem master cylinder.
  • the slide 6 is designed as a hollow slide and has an inner opening 33 which extends in the longitudinal direction 4.
  • the slide 6 has on its outer circumference a first control edge 34 which interacts with a corresponding control edge 36 of the sleeve-shaped housing body 2 and thereby releases or closes a variable throttle cross section 38 between the connection 32 for the high pressure source and the inner longitudinal opening 33 of the slide 6.
  • the control edge 34 delimits an annular groove 40, which is provided concentrically in the outer peripheral surface of the slide 6.
  • the groove 40 communicates via two radial bores 42 with the inner longitudinal opening 33 of the Slide 6.
  • a slowly displaceable pressure piston 48 is provided in the inner longitudinal opening 33, which is acted upon at one end by the pressure of the high-pressure source prevailing in the inner longitudinal opening 33 and at the other end - like the slide 6 - with its end face 50 against the armature 14 supports.
  • a slowly displaceable pin 52 engages from the outside in the inner longitudinal opening 33 of the slide 6.
  • the pin 52 has at its free end 54 a sealing pin 56 which, in the illustrated normal braking position, bears against a sealing seat 58 of a seat valve 60 which closes the pressure medium connection 28 of the low-pressure accumulator.
  • the pin 52 has a radial collar 62 located outside the longitudinal opening 33.
  • a spiral spring 64 surrounding the pin 52 is supported at one end against this collar 62 and at the other end against the end face 66 of the slide 6, so that the pin 52 in Direction is biased to the sealing seat 58.
  • Spring 64 and collar 62 are located within a cup-shaped element 68, which rests with a collar-shaped flange section 70 against the end face 66 of the slide 6 and has a bottom opening 72 through which the pin extends so as to be longitudinally displaceable.
  • the bottom region 74 of the cup-shaped element 68 forms a stop 76 for the radial collar 62 of the pin 52 and therefore forms a displacement end position for the pin 52.
  • a slowly displaceable pressure and sealing piston 78 which is acted upon at one end by the pressure prevailing in the inner opening 33 and at the other end abuts against the end 80 of the pin 52 which engages in the longitudinal opening 33.
  • the illustrated multi-way pressure regulating valve works as follows: In the drawing of the figure, the armature 14 and thus the slide 6 are under the pretension of the spring 8 in their first end position. There is a pressure medium connection between the connection 32 of the high-pressure source and the connection 30 of the wheel brake, in which the variable throttle cross-section 38 is opened to a maximum in the area of the connection 32, so that pressure medium via the annular groove 40, the transverse bores 42 into the inner longitudinal opening 33 and over the inclined holes 46 to the annular groove 44 and Pressure medium connection 30 of the wheel brake can reach.
  • the pressure and sealing piston 78 is also moved back and forth under the effect of the control pressure and holds the sealing pin 56 of the pin 52 in sealing contact with the sealing seat 58 by pressing on the pin 52 Seat valve 60.
  • the pin 52 is therefore supported on the sealing seat 58.
  • a control edge 82 which is formed by the end face 66 of the slide 6, passes over a corresponding control edge 84 of the housing body 2, whereby a throttle cross-section, not shown in the figure but easily imaginable, is opened between the pressure medium connection 30 of the wheel brake and the opened seat valve 60 to cause a pressure reduction in the wheel brake to the low pressure accumulator.
  • control edge 82 of the slide 6 passes over the control edge 84 in the opposite direction, so that the throttle cross section between the wheel brake and the low-pressure accumulator is interrupted again, the seat valve 60 still remaining open. If the pressure in the wheel brake is to be increased again, the current in is controlled accordingly the coil 26, the armature 14 is moved so far to the left under the action of the spring 8 until the control edge 34 of the slide opens the control edge 36 again in the region of the pressure medium connection 32 to the high pressure source.
  • the sealing and pressure piston 78 is supported on the housing via the pin 52, the collar 62, the stop 64, the collar 70 and the spring 10.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetism (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Regulating Braking Force (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

Cette vanne de régulation à plusieurs voies à commande électromagnétique pour systèmes hydrauliques de freinage de véhicules à moteur à système anti-patinage permet de mettre au moins un frein de roue (roue) en communication hydraulique avec une source de haute pression (THZ) ou un réservoir à basse pression (NDS) et comprend une coulisse (6) guidée dans un corps cylindrique de boîtier (2) et précontrainte dans les deux directions dans le sens longitudinal de déplacement (4), ainsi qu'une ouverture allongée (33) dans le sens longitudinal. Pendant le mode de fonctionnement normal des freins, la coulisse (6) est précontrainte dans la direction d'une première position extrême dans laquelle le frein de roue est en communication fluide avec la source de haute pression et coupé du réservoir à basse pression. Une vanne (60) située entre le frein de roue et le réservoir à basse pression s'ouvre pour réduire la pression dans le frein de roue. Afin d'éviter que la coulisse (6) ne se bloque dans le mode de fonctionnement normal des freins, la vanne à plusieurs voies comprend un piston de compression (48) mobile en sens longitudinal dans l'ouverture (33) de la coulisse (6). Dans le mode de fonctionnement normal des freins, ce piston (48) s'oppose avec son extrémité libre (50) à la première précontrainte qui s'exerce dans la direction de la première position extrême, de sorte que la coulisse (6) puisse se déplacer en avant et en arrière dans le sens longitudinal en fonction de la pression de la source de haute pression.
PCT/EP1998/000444 1997-02-01 1998-01-28 Vanne de regulation de pression WO1998033688A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19703775.5 1997-02-01
DE1997103775 DE19703775A1 (de) 1997-02-01 1997-02-01 Druckregelventil

Publications (1)

Publication Number Publication Date
WO1998033688A1 true WO1998033688A1 (fr) 1998-08-06

Family

ID=7819020

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1998/000444 WO1998033688A1 (fr) 1997-02-01 1998-01-28 Vanne de regulation de pression

Country Status (2)

Country Link
DE (1) DE19703775A1 (fr)
WO (1) WO1998033688A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008143188A1 (fr) 2007-05-17 2008-11-27 Bridgestone Corporation Pneu à carcasse radiale pour charge lourde

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005038215A1 (de) * 2005-05-06 2006-11-09 Continental Teves Ag & Co. Ohg Mehrwegventil
DE102015223833A1 (de) * 2015-12-01 2017-06-01 Continental Teves Ag & Co. Ohg Bremsanlage

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3832010A (en) * 1971-12-13 1974-08-27 Citroen Sa Brake control devices for preventing locking a braked wheel
JPH072076A (ja) * 1993-06-21 1995-01-06 Hitachi Ltd アンチロックブレーキ装置の流量制御弁
DE4441150A1 (de) 1994-11-18 1996-05-23 Teves Gmbh Alfred Druckregelventil

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2669883B1 (fr) * 1990-11-29 1993-01-29 Bendix Europ Services Tech Dispositif de freinage automatique pour vehicule.
FR2691690B1 (fr) * 1992-05-26 1994-07-22 Bendix Europ Services Tech Dispositif de freinage a distributeur unique pour antiblocage et antipatinage.

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3832010A (en) * 1971-12-13 1974-08-27 Citroen Sa Brake control devices for preventing locking a braked wheel
JPH072076A (ja) * 1993-06-21 1995-01-06 Hitachi Ltd アンチロックブレーキ装置の流量制御弁
DE4441150A1 (de) 1994-11-18 1996-05-23 Teves Gmbh Alfred Druckregelventil

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 095, no. 004 31 May 1995 (1995-05-31) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008143188A1 (fr) 2007-05-17 2008-11-27 Bridgestone Corporation Pneu à carcasse radiale pour charge lourde

Also Published As

Publication number Publication date
DE19703775A1 (de) 1998-08-06

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